Pumping system



Dec. 13, 1955 p, DAVIDSON 2,726,606

PUMPING SYSTEM Filed July 16, 1951 5 Sheets-Sheet 1 Ar/hu/ P. Dov/(Ls 0/7 INVENTOR.

Dec. 13, 1955 A. P. DAVIDSON PUMPING SYSTEM 5 Sheets-Sheet 2 Filed July 16 1951 Arfhur F. Dowdson INVENTOR.

ATTORNEY Dec. 13, 1955 A. P. DAVIDSON 2,726,606

PUMPING SYSTEM Filed July 16, 1951 5 Sheets-Sheet 3 Arf/iur P [70100800 INVENTOR.

A TTORNE Y A. P. DAVIDSON PUMPING SYSTEM Dec. 13, 1955 5 Sheets-Sheet 5 Filed July 16, 1951 Arf/n/r f? Dav/c2600 INVENTOR.

United 8...... Patent 2,726,606 PUMPING SYSTEM Arthur P. Davidson, Mercedes, Tex. Application July 16, 1951, Serial No. 236,988

8 Claims. (Cl. 103-87) This invention relates to a pumping system wherein means are provided for handling fluids, and in particular, well fluids.

In the past considerable effort has been made to improve and produce new systems of pumping because it has been recognized that the known pumps and pumping systems have an extremely low efliciency as measured in terms of the work output obtained from work input. Furthermore the speed range on pumps known today are limited within a narrow range due to the fact that it is only within that narrow range of speed that an economical and satisfactory efliciency can be obtained. It has been observed by some engineers and others working with pumps and pumping systems that turbulence such as is created in a centrifugal pump causes a large Waste of power, and until this invention it was not appreciated how the turbulence could be reduced so as to prevent the Waste of power and to obtain an efliciency of 98 to 99 per cent and a speed range in which the efliciency remains substantially that high throughout a 15,000 to 18,000 R. P. M. variation.

It is, therefore, an object of this invention to provide a pump and pumping system in which the turbulence of the fluids being pumped is reduced to a minimum and thereby substantially all of the power input to the pump and pumping system is recovered in the form of power output so that efliciencies as high as 98 to 99 per cent are obtainable.

It is another object of this invention to provide a pump and pumping system in which the speed range is relatively unlimited due to the fact that the efliciency of the pump' and pumping system remain practically the same throughout a speed range of 15,000 to 18,000 R. P. M.

Another object of this invention is to provide a pumping system in which an actuating fluid is fed under high pressure from a first area to a confined space in a second area to create at the second area rotated shaft power.

Another object of this invention is to provide a pumping system wherein an actuating fluid is pumped from one area to a confined space in the second area in which confined space a fluid driven motor and interconnected pump are located for pumping fluids from the confined space.

Another object of this invention is to provide a combination fluid driven motor and associated pumping unit which may be located within a confined space such as a well bore for use in pumping operations such as deep well pumping.

Another object of this invention is to provide a fluid driven motor or a pumping unit which has alternately spaced impeller units and continuity control sections.

Another'object of this invention is to provide a new type of pump auger or impeller which may be described as an inverse modified slightly spiral turbinate section or unit.

Another object of this invention is to provide a fluid driven motor in which the new type of pump auger or impeller is used in combination with a continuity control section or a unit.

Another object of this invention is to provide a pumping system wherein a combination fluid driven motor and pump are located within a well bore or similar confined space, and the motor has included therewith a new type auger blade or impeller, and the pump also has included therewith a new type of auger blade or impeller.

Other and further objects will be readily apparent when the following description is considered in connection with the accompanying drawings, wherein:

Fig. 1 is a diagrammatic view of the overall pumping system,

Fig. 2 is a sectional view illustrating the combination fluid driven motor and pumping unit in which both the motor and the pumping unit utilize an alternate arrangement of the continuity control section and turbinate units of this invention,

Fig. 3 is a section taken on line 3-3 of Fig. 2 and i1- lustrating the web supported bearing and the entry of the fluid feed tube for fluid driven motor of Fig. 2,

Fig. 4 is a section on line 4-4 of Fig. 2 and illustrating the arrangement of the continuity control section,

Fig. 5 is a section on line 5-5 of Fig. 2.and illustrating the bearing support and well fluid inlet which may be used with the combination shown in Fig. 2,

Fig. 6 is a section taken on line 66 of Fig. 2 and illustrating the details of the entry of the fluid feed tube,

Fig. 7 is a section taken on line 77 of Fig. 2'and illustrating a fairing used in the inlet portion of the motor of Fig. 2,

Fig. 8 is a perspective view partly in section illustrating the type of continuity control section or unit used in the combination of Fig. 2,

Fig. 9 is a section taken on line 9-9 of Fig. 8 illustrating the shape of the vanes of the continuity control section of Fig. 8,

Fig. 10 is a sectional view illustrating the details and structural relationship of the continuity control section and the turbinate units of this invention,

Fig. 11 is a section taken on line 11-11 of Fig/10 and illustrating the relationship of the turbinate unit and the continuity control section vanes,

Fig. 12 is an elevation view of a dual blade pumping element of this invention,

Fig. 13 is a section illustrating the details of the pump shaft bearing and washer seal assembly,

Fig. 14 is a sectional view illustrating a modification of the combination of Fig. 2 in which the actuating fluid is fed through the fluid driven motor,

Fig. 14a is a section taken on line 14a14a of Fig. 14 and illustrating an alternative bearing support in the nature of a web-like structure,

Fig. 15 is a sectional view illustrating a modification of the combination of Fig. 14 in which turbinate units are carried in staggered alternate relationship to each other on both a hollow inner shaft and a tubular outer housing in the motor, and the power is transmitted to the pumping unit through a solid shaft connected to the hollow inner shaft which extends beyond and below a sleeve interconnected with the tubular housing, both the sleeve and the solid shaft carrying pumping turbinate units thereon,

Fig. 16 is a modification of the combination shown in Fig. 15 wherein conventional turbine blades are substituted for the novel turbinate units of Fig. 15 in the motor and wherein the outer housing of the pumping unit is an extension of the tubular housing of the motor so that alternately arranged pumping blades are carried by the solid shaft of the pump and the pump housing both or" which rotate,

Fig. 17 is a sectional view which illustrates in detail the arrangement of the turbinate units on the pumping unit of Fig. 16,-

Fig. 18 is an elevation of the turbine blade arrangement used in the fluid driven motor of Fig. 16,

Fig. 19 is a section taken on line 1919 of Fig. 18 and illustrating the curvature of a typical turbine blade unit.

Following is a detailed description of this invention wherein like parts are referred to by like numerals in all figures of the drawings.

Referring now to Fig. 1 wherein a combination for pumping fluids is illustrated it can be seen that the pumping is illustrated as occurring within a well bore 25 having a casing 26 therein.. It is to be understood that this pumping system of this invention is not limited to use in a well bore but may be used in pumping fluids from one area to another and is particularly suitable for pumping from a confined space such as in a well bore or in restricted spaces which may be found in industrial and ship installations. Thus the well bore 25 may in some instances be a ship tank for example. Itis believed readily apparent that this pumping system illustrated in Fig. 1 could be used in confined spaces other than a well bore such as well bore 25 but the operation and combination of this pumping system will be described only in connection with the well bore 25 since the operation and combination will be similar when used in other confined spaces.

In fact, the motor 37 could be used without the pumping unit 39 at locations remote from the surface pump 33 as a source of power for operating tools and devices other than the pumping unit 39.

At the surface 28 of the well it is preferable to locate a reservoir 30. This reservoir 30 holds a source of actuating fluid which is fed through the surface inlet pipe 31 to a surface pump 33. The surface pump 33 is driven by any suitable prime mover 35 such as a gasoline or diesel engine. The pump 33 may be of the centrifugal type or even of the reciprocating type, but it is preferred that the pump 33 be of the same type as the pump used in the confined space such as well bore 25 and which will be more fully described hereinafter.

If desired the pump 33 may have in connection therewith a conventional priming tank and valve set up not shown so that the pump 33 may be primed in the event that the water or other fluid cannot be drawn from the reservoir 30 upon actuation of the pump 33. The actuating fluid from the pump 33 located on the surface 28 is fed through the support pipe 36 into the fluid driven motor 37 located within the well casing 26. The actuating fluid being fed to the fluid driven motor 37 is under considerable pressure from the pump 33 and it is' this pressure in the form of kinetic energy of the'fluid being pumped which imparts the energy to the blade or turbinate unit of the fluid driven motor 37. As the actuating fluid passes through the motor 37 its kinetic energy is transformed into rotated shaft power in the motor 37 and the pressure and kinetic energy of the actuating fluid being fed from the pump 33 is thus dissipated by passing through the motor 37. A more detailed explanation of the motor 37 will be set forth hereinafter. However, it will be noted from Fig. 1 that the actuating fluid is fed beneath the motor 37 and passes upwardly therethrough so that it enters into the well casing 26 above the motor 37 after the majority of its kinetic energy has been spent.

To prevent the actuating and pumped fluid from returning into the well, packers 38 may be inserted between the casing 26 and the housing 70 of the motor 37 These packers 38 may be of conventional construction. The rotating action of the motor 37 is transmitted through a shaft 40 to the pumping unit 39 therebelow. Immediately below the pumping unit 39 is positioned a strainer or screen 42 through which thewell fluids pass into the pumping unit 39. The pumping unit 39 discharges its water above itself into the well casing 26 so that it passes around the motor 37 and intermingles with the actuating fluid being discharged from the motor 37. Thus the fluid 4. which is returned to the surface through the discharge pipe 43 and into the reservoir 30 is the combined amount of actuating fluid fed to the motor 37 and the well fluid being pumped by the pump 39. For example, if the feed pump 33 were feeding actuating fluid at the rate of approximately 500 gallons per minute then the discharge from the motor 37 would also be 500 gallons per minute, and under normal circumstances'the amount of well fluid being pumped by the pumping unit 39 would be approximately 1500 gallons per minute so that the total delivery to the discharge pipe 43 and the reservoir would be approximately 2000 gallons per minute. The excess of fluid pumped would then be released from the reservoir through the reservoir outlet pipe 4.4 which of course may be controlled by suitable valve and tank arrangements. Should the reservoir 30 need to be filled a filling pipe 45 may be provided for accomplishing this. It is to be understood that the source of actuating fluid may be separate from the reservoir 30 if desired.

One of the main reasons for the high etficiency obtainable with the motors and pumps of this invention is due to the structure of the turbinate units 46 illustrated in Figs. 10 and 17. These turbinate units 46 may be basically described as an auger type of impeller. However, this term is not an accurate description of the turbinate units 46 of this invention. The conventional auger type of impeller was not found to be entirely satisfactory and due to the excessive slippage range the conventional auger type of impeller does not provide a uniform flow of fluid through the pump. In an efliort to overcome the side slippage and lack of uniformity in the movement of the water or other fluid by the auger the turbinate units 46 of this invention were developed. It was conceived that the difficulty with the flat auger resulted from the fact that the periphery of the auger was traveling at a much greater speed than the portion of the auger blade near the hub or center shaft. Thus the flat auger tends to throw the water or other fluid toward the housing or periphery of the auger blade in a similar manner to a centrifugal acting pump. This action of. throwing causes turbulence in the fluid being pumped and results in an extreme waste of power. The ideal way in which to move fluids is by, in effect, slicing through the fluid to move the sliced portion forward without turbulence. The conventional auger has the slicing effect but as explained it also has extreme turblence which is very undesirable in pumping. The turbinate units of this invention can most aptly be described as an invert modified slightly spiralled turbinate section. The word turbinate means an inverted cone or an object shaped like a top. It will be observed from the Figs. 10 and 17 that the outer edges of the turbinate units 46 are sloped upwardly so that if a line were drawn tangent to that slope and an opposite line were drawn on the-portion of the unit 46 on the other side of the shaft the two lines would converge at a point C, such as shown in Fig. 12, and the point D in Fig. 10, which points'will be substantially in the center of the shaft line. It will be appreciated that the slope of the outer periphery of the turbinate unit 46 may be varied to accommodate different sizes of pumps; for example, on a very small diameter pump the taper from the outside periphery of the turbinate units 46 may be inclined so that they form a true cone from the outer periphery to the center of the shaft. The main purpose of this sloping of the turbinate unit at the periphery is to obtain a uniform flow of fluid through the pump or motor and to prevent any turbulence in the movement of the fluids therethrough. Since the periphery of the turbinate unit 46 travels at a. considerably higher rate of speed than the portion of the blade near. the center of the. shaft or hub it is believed apparent that the diflference in movement of the water or fluid in thepump will result in turbulence as previously mentioned. By sloping or angling the outer periphery of the turbinate unit 46 in a manner as shown in Figs. 10, 12, and 17, the resultant force vector of the outer periphery of the turbinate unit is toward the center of the shaft. Thus the amount of fluid being pumped will be substantially the same throughout the turbinate blade area since the portion of the fluid being pumped by the periphery of the turbinate unit 46 will be combined with that portion pumped by the blade nearer to the shaft 40 or hub 48. By thus moving a portion of the periphery fluid toward the center and thereby moving substantially the same amount of water or fluid throughout the entire turbinate unit area a uniformity without turbulence results. Therefore, the term turbinate unit as used herein and in the claims refers to an auger type of impeller blade wherein a portion of the outer edge thereof is inclined more toward the center of the blade than the rest of the blade, whereby substantially the same amount of fluid is moved by allparts of the blade during its rotation.

In some cases it may be desirable to have a multiple blade turbinate unit such as illustrated in Fig. 12. In Fig. 12 is shown a dual bladed turbinate unit 50 mounted on a hub 51 which in turn is mounted on a shaft 52. It will be observed that both the single blade turbinate unit 46 in Fig. and the dual bladed unit 50 in Fig. 12 are shown as being keyed to the shaft 40 by the key 53. Of course, the key way may be replaced by any other equivalent means of securing the hub 48 or 51 to the shaft 40 or52 respectively. For example it may be a splined shaft arrangement or preferably a tapered wedge type of locking means.

In the dual bladed turbinate unit 50 the blades are started 180 degrees from each other at the same level on the shaft 51 as can be seen in Fig. 12. Thus blade 54 makes one complete revolution and ends directly above its leading edge. Likewise blade 55 which is positioned 180 degrees from the leading edge of blade 54 makes a complete 360 degree revolution and has its trailing edge ending directly above its leading edge. It should also be pointed out that the blades in the single turbinate unit 46 and in the dual turbinate unit 50 have a feathered or knife-like leading edge at their periphery, which knifelike edge is shown at 56 in turbinate unit 46 and at 57 and 58 in the dual turbinate unit 50.

Turbulence in pumping may be further reduced in some cases by the use of continuity control sections 60, which are shown in Fig. 10 as being spaced alternately with respect to the turbinate units 46. The term continuity control sections as used herein and in claims refers to fluid guide vanes which serve to direct fluid flow axially through a pump or motor housing and which are radially positioned about a pump or motor shaft. Of course, these continuity control sections 60 may be used with either the single turbinate unit 46 or the multiple turbinate units 50. In Fig. 11 the vanes 62 are shown dotted underneath the turbinate unit 46. The vanes 62 are integral with or secured to the tube 63 at their outer edges and to the support hub 64 at their inner edges. Thus each continuity control section 60 may be handled as a separate unit and replaced as such. Thus, for example, the continuity control sections 60 may be fitted within the tubular support 65 as shown in Fig. 2 or, if desired, the tube 63 as shown in Fig. 10 may be modified to the form 66 shown in Figs. 14, wherein the tube 66 has a set of outer threads 67 and a set of inner threads 68 at opposite ends for threading into the next adjacent continuity control section or other type of sleeve unit such as the housing 70 shown in Fig. 14.

The turbinate units 46 or the multiple turbinate units 50 are positioned so that the blades of the turbinate units 46 have very little clearance with the adjacent edges of the vanes 62 of the continuity control sections 60. Thus there is little opportunity for turbulence to be created prior to the fluids entering and passing through the continuity control sections 60. Because of the arrangement of the vanes 62 any slight turbulence which may be created in pumping will be eliminated in the passing of the fluid 6 through the continuity control sections-60. In Figs. 8 and 9 the details and perspective of the vanes 62 can be clearly seen as well as the relationship of the vanes 62 with the support hub 64 and the tube 63. In Fig. 9 it can I be seen that the vanes in cross-section are tapered or feathered to reduce the skin-friction and possible turbulence which might be created by a blunt or squared vane 62. The feathered or knife-like edges 71 thus cut into the fluid being passed therethrough and reduce to a minimum any friction or turbulence.

Referring now to Fig. 2 wherein is shown one type of fluid driven motor and pump combination of this invention for use in deep well pumping or other confined spaces, as has been previously mentioned, the entire combination of the motor 37 and the pump 39 are placed within the casing 26 in the well bore 25. In Fig. 2 the casing 26 has been shown only partially for clarity as the entire relationship of the casing 26 and the motor 37 and pump 39 may be seen in Fig. 1. The actuating fluid from the surface pump 33 shown in Fig. 1 passes through the feed tube 36 and then into a separate actuating fluid tube 75. The actuating fluid tube 75 passes through a plate 76 that is shown in Fig. 6 and is then stopped so that the fluid subsequently passes into the chamber defined by the baffle plate 77 and the housing 70. The lower limit of the actuating fluid is defined by the curved baifle guide 78 which directs the actuating fluid upwardly from its previous downward travel. To reduce the friction and to prevent turbulence of the actuating fluid as it is entering the motor 37 a fairing 79 has been provided on the shaft 49. Inserted between the shaft 40 and the fairing 79 may be a brass or other suitable metal sleeve 80. The actuating fluid then passes beyond the fairing 79 through the first continuity control section 60 and into the first turbinate unit 46 and thus continues on through the motor 37. The kinetic energy of the actuating fluid being imparted to the turbinate unit 46 to cause rotation of the shaft 44 After the actuating fluid has passed through the motor 37, it passes out through the top thereof and finally through the opening 82 in the housing 70. The shaft 40 is supported in a rubber bearing 83 at its uppermost point and may have additional bearing such as bearing 85.

A detailed structure of the bearing which may be used for supporting the shaft 40 and taking the thrust thereon is shown in Fig. 13. There the bearing 85 receives a narrowed smaller portion 88 of the shaft 40, and the bearing 85 is inserted within an opening 89 in a spider 90. This spider 90 may take the form shown in Figs. 2, 5, and 13, wherein openings 91 are provided for the well fluid to pass through, or it may take the form of the web members 92 as shown in Figs. 14 and 14a. The web structure is generally preferred since there is more open area for the well fluid to pass therethrough. Referring again to Fig. 13, it can be seen that a seal 95 has been provided in which an inner O-seal ring 96 and an outer O-seal ring 97 are utilized. To prevent the seal and bearings from disengaging from the spider 90 a ring washer 98 is inserted within a groove 99 in the spider 90.

The upper rubber bearing 83 is likewise supportable by web members 100 as is best seen in Fig. 3. It will be understood that additional bearings such as the one positioned at 84 may be utilized as desired in order to reduce the vibration and to provide the maximum of efliciency.

Referring again to Fig. 2, therein is shown the shaft 46 which continues through the fluid-driven motor 37 and into the pumping unit 39. Since the turbinate units 46 are splined or otherwise secured to the shaft 40, when the actuating liquid or fluid turns the turbinate units 46 in the motor 37 the shaft 40 is rotated to impart rotation to the turbinate units 46 positioned on the shaft 40 in the pumping unit. In this modification of Fig. 2 all of the turbinate units 46 will have the same handedness; that is, if the turbinate units 46 of the motor 37 are right handed then the turbinate units 46 of the pumping unit 39 will also be right handed. As can be seen theturbinateunits, 46.- are positioned in approximately the same manner as. the turbinate units 46 of the motor 37 with respect to the continuity control sections 61). When the continuity control sections 60 are utilized as shown in Fig. 2 in the motor 37 and the pump 39 they are held in place by locking rings such as the locking ring 101 in the pump 39 and the locking ring 102 in the motor 37. When the turbinate units 46 of the pump 39 are rotated by the actuation of the motor 37 the fluid in the well or other confined space within which this combination is located will pass upwardly through the opening 91 and into the pump chamber 103 and will then be forced upwardly in a continuous manner without turbulence by the turbinate units 46 and will pass through the continuity control sections until the top of the pumping unit 39 is reached at which point the well fluid passes into the channel 1115 created by the area between the housing 70 and the tubular support 75. Thus the well fluid. being pumped passes on the outer edge or outer surface of the motor 37 and finally merges with the dissipated actuating fluid from the motor 37 at a point just below the opening 82 through which both discharge together into the casing area thereabove and thus continue onwardly until they reach the outlet pipe 43 as shown in Fig. 1.

In the modification of the combination motor 37 and pump 39 shown in Fig. 14 the actuating fluid passes downwardly through a hollow shaft 110. The actuating fluid passes through opening 111 in the hollow shaft 110 and upwardly into fluid driven motor 37 beyond the continuity control section 60 and driving the turbinate units 46 and then subsequently passing out of the top of the motor 37 and through the openings 82 in housing 70. Bearings are provided at 112 and 113 for the hollow shaft 110. Appropriate seal rings 114 and 115 are positioned above and below the bearing 112, and similar seals are provided above and below the bearing 113 to prevent the fluid, both the actuating fluid and the fluid being pumped, from damaging the bearings. At the lower portion of the tubular support 65 where the actuating fluid passes through the openings 111 the tubular support 65 may have ridges or guide protrusions for causing the water or other fluid to begin its flow in a relatively straight line to thus further reduce any turbulence which may be present. The actuation of the motor unit 37 is transmitted from the hollow shaft 110 to a solid shaft 117 which is threadedly or otherwise affixed to.the hollow shaft 110 below the opening 111 therein. Thus the turbinate units 46 in the pump 39 will have the same handedness and will rotate in the same direction as the turbinate units 46 of the motor 37. The well fluid being pumped by the pumping unit 39 will pass upwardly through the pump chamber 103 and into the channel 105 defined by the housing 70 and the tubular support 65 and then outwardly and mingles with the actuating fluids which have been dissipated in passing through the motor 37. Thus the combined flow of well fluid and dissipated actuating fluids will be returned to the surface.

In Fig. 15 the hollow shaft center feed type of motor is utilized as in Fig. 14. Thus the actuating fluid is fed through a hollow shaft 110 and outwardly through openings 111 at the bottom of the motor 37 and then passing upwardly through the motor and outwardly through opening 120 and then through openings 82 in the housing 70. The main difference between the modifications of Fig. 14 and Fig. 15 is that in Fig. 15 there are no continuity control sections 60 but instead they have been replaced by turbinate sections 46 which have an opposite handedness to the turbinate units 46 located on the hollow shaft 110. Furthermore the turbinate units 46 on the tubular sleeve 45 are capable of transmitting a rotated action because the tubular sleeve 65 is made rotatable in this modification. Thus in addition to the bearings 112 a bearing 122 is also used for the tubular support 65. As the actuating fluid passes through the motor 37 the fluid contacts first one set of turbinate units then another, and since the turbinate units on the tubular support 65 are interfitted in the spaces: between the turbinate units 46. on the hollow shaft 110 there is a continuous exertion of force on the turbinate units as the actuating fluid passes through the motor 37. Thus the hollow shaft 110 will be turning in one direction andthe tubular support 65 will be rotating in the opposite direction so that there is a counterrotation of these two elements. Likewise this counterrotation is transmitted to the pumping unit 39 because the hollow shaft 111 is connected with the solid shaft 117 and the tubular support 65 is. connected with a sleeve 125. The sleeve extends only half of the distance into the pump 39 so that it carries the upper half of the turbinate units 46 of the pump 39 while the solid shaft 117 extends beyond the sleeve 125 and carriesthe. other half of the turbinate units 46 thereon. Of course, the turbinate units 46 carried by the sleeve 125 will have the same handedness as the turbinateunits 46 on the tubular support 65 whereas the turbinate units 46 located on the solid shaft 117 will have the same handedness as the turbinate units 46 on the hollow shaft 110. Thus even though there is a counterrotation of the hollow shaft 110 and interconnected solid shaft 117 with respect to the tubular support 65 and sleeve 125 due to the opposite handedness of the turbinate units, the direction of flow in the pumping unit 39 will be the same for all of the fluids passing therethrough. As in the other modifications the fluid pumped from the well will pass upwardly through the channel and outwardly through 82 intermingling and mixing with the dissipated actuating fluid from the motor 37. The bearing 85 in Fig. 15 is similar in structure to the bearings 35 in Figs. 2 and 14 but will obviously be modified in order to accommodate the different shaft structure. Of course, there will be an additional bearing 85 at the lower end of the solid shaft 117 not shown.

Fig. 16 shows a modification of the combination fluid driven motor 27 and pump 39 which diflfers from the modification of Fig. 1 5 primarily in that the tubular support 65 is flared outwardly at 126 and is integrally or otherwise secured to the outer turbinate support 128.

Another difference between the modification of Fig. 15 and that of Fig. 16 is in the substitution in Fig. 16 of the turbine blades 129 which are fixed to the hollow shaft and rotate therewith while turbine blades 130 alternately disposed with respect to the turbine blades 129 are positioned on tubular collar 131 which are formed together and integrally or otherwise connected to the tubular support 65. Thus as the actuating fluid passes downwardly through the openings 111 and is directed upwardly by the guide baffle 133 the actuating fluid is directed from one set of turbine blades 129 to the adjacent set of blades 130 and onwardly until the actuating fluid reaches the opening in the tubular support 65 and then passes outwardly through the opening 82.

It will be appreciated that the turbine blades 129 and illustrated in Figs. 16 and 18 as well as the top view shown in Fig. 19 may be utilized in place of the turbinate units 46 used in the modification of Fig. 15. However, it should be emphasized that the turbinate units 46 are far superior in efliciency and have considerably less turbulence than that of the turbine blades 129 and 130, so that in most instances it will be preferred to use the turbinate units 46 as shown in Fig. 15.

The actuating fluid in passing through the motor 37 of Fig. 16 will, of course, turn the hollow shaft 110 which will in turn rotate the solid shaft 117 connected therewith. Since the turbine, blades 1 30 are curved in the opposite direction from the turbine blades 129. the hollow shaft 110 and the tubular support 65 will turn in the opposite direction. Thus the support 128 and the solid shaft 117 will. also turn in opposite directions. In order to have all of the turbinate units 46 used in the pump 39 working in the same direction it will, therefore, be necessary to have the turbinate. units 3'6 on the solid shaft 117 of an opposite handedness to the turbinate units 46 on the support 128.

Details of the support or sleeve 128 have been shown in Fig. 17 and therein it can be seen how the turbinate units 46, which are connected to the sleeve 128 at their periphery, are provided with openings 140 in order to permit the hub 48 of the turbinate units 46 located in the shaft 117 to pass through the center of the turbinate units 46 located on the support or sleeve 128. If desired, the turbinate units 46 used in the pump 39 of Fig. 16 may be replaced by turbine blades 129 and 130 as shown in detail in Fig. 18. However, since the turbinate units 46 are by far the most eflicient the turbine blades 129 and 130 are not preferred.

The keys 53 mentioned previously for securing the hub of the turbinate unit 46 to its shaft have been shown again in Figs. 17 and 18 in order to secure the turbinate units 46 to the shaft 117 and the turbine blades 129 to the shaft 110.

In Fig. 19 the top view of the turbine blade 129 is shown in which the vanes 142 are illustrated in their conventional form. The turbine blade 130 will be of the opposite handedness so that there will be a continuous flow from one set of blades to the other while the fluid is passing through the motor 37 or while the fluid is being pumped by the pump 39 if the turbine blades 129 and 130 are utilized in that type of modification.

In the modification of Fig. 16 since the sleeve 128 is exterior of the solid shaft 117 an extra bearing 145 must be provided and the solid shaft will again be supported by a bearing 85 as previously described. The top bearings will be of the same arrangement as the bearings 112 and 122 of Fig. 16 and will likewise have seals to prevent the fluid from damaging them.

It is believed readily apparent from the above description that an apparatus and system has been devised which will provide an efliciency as high as 98 to 99 percent in many cases due to the fact that the turbinate units 46 of the multiple turbinate units 50 are especially constructed and so combined with the continuity control section 60 in their use in a motor or a pump that the turbulence of the fiuids passing therethrough is reduced to a minimum.

Furthermore, it is believed readily apparent that a combination fluid driven motor and pump have been devised for use in confined spaces such as well bores where previously electric motor drives or similar equipment subject to excessive damage and requiring extreme measures to prevent the fluid being pumped from entering into the motor were used.

Broadly, this invention contemplates a pumping system wherein an actuating fluid is fed under high pressure from a first area to a confined space, such as a well bore, in a second area and creating rotative shaft power in that confined space by the energy imparted from the actuating fluid.

What is claimed is:

1. In a combination fluid driven motor and pumping unit,-a shaft interconnecting said motor and said pumping unit, said shaft having a hollow portion in the motor for conducting fluid to said motor for actuating same and having a solid portion therebelow in the pumping unit, spaced impeller units on said shaft in said motor, a tubular support rotatably mounted about said hollow portion of said shaft and said impeller units in said motor, impeller units on said tubular support rotatable by said fluid to impart rotation to said support, said tubular support being necked down between said motor and said pumping unit so that a sleeve is formed about said solid portion of said shaft in said pumping units, said shaft having a lower reach extending beyond said sleeve, impeller units on said sleeve and said lower reach of said shaft to form the pumping elements of said pumping unit, said pumping elements being rotated upon rotation of the impellers on the shaft and on said support.

2. In a combination fluid driven motor and pumping unit, a shaft interconnecting said motor and said.

pumping unit, said shaft having a hollow portion in the motor and having a solid portion in the pumping unit, spaced turbinate units on said shaft in said motor, a tubular support about said hollow portion of said shaft and said turbinate units in said motor, said tubular support being extended to form an outer housing support for said pumping unit, spaced turbinate units on said tubular support in said motor interfitting between said turbinate units on said hollow portion of said shaft in said motor, spaced turbinate units on said solid portion of said shaft in said pumping unit, and spaced turbinate units on said outer housing support to interfit between said turbinate units on said solid portion of said shaft.

3. A combination fluid driven motor and well pump adapted to be lowered into a well bore with the motor being actuated by fluid supplied from the surface of the well, comprising a support pipe adapted to be suspended in the well bore, a housing for said motor and said pump connected to the lower end of said support pipe,

a shaft extending axially through said housing and connected thereto, a tubular member disposed about said shaft in the upper end of said housing for forming the outer surface of the motor with an annular space between said tubular member and said housing, means connecting said tubular member to said housing for permitting rotation of said tubular member relative to said housing, a fluid conductor in said housing having communication with said support pipe and the lower end of said tubular member for directing an actuating fluid flowing from said support into said tubular member in an upward direction, motor impeller blades on said shaft and within said tubular member for actuation by the fluid admitted into said tubular member, additional motor impeller blades on said tubular member also adapted to be actuated by said fluid admitted into said tubular member to rotate said tubular member relative to said housing, a tubular extension on said tubular member extending downwardly therefrom and rotatable therewith, pump impeller blades on said extension adapted to be rotated therewith for pumping well fluid upwardly through said housing, and additional pump impeller blades connected to said shaft in said housing below said tubular member and adapted to be rotated with said shaft upon the actuation of said motor impeller blades whereby well fluid in the well is pumped upwardly through said housing by both said pump impeller blades and said additional pump impeller blades.

4. The structure set forth in claim 3, wherein said tubular member has a discharge opening, and said housing has an outlet into the well bore at its upper end in communication with said discharge opening whereby the actuating fluid may be returned through the well bore to the surface of the well.

5. The structure set forth in claim 3, wherein said tubular member has a discharge opening at its upper end,

said housing has an outlet into the well bore at its upper end in communication with said discharge opening whereby the actuating fluid may be returned through the well bore to the surface of the well, and said housing has an opening above said pump impeller blades communicating with said annular space so that the well fluid is also discharged from the housing outlet into the well bore.

6. The structure set forth in claim 3, wherein said shaft extends below said tubular extension, and wherein said pump impeller blades on said tubular extension are positioned above said additional pump impeller blades on said shaft.

7. A pump and motor adapted to be lowered into a well bore, comprising a housing, sealing means on the housing for sealing off the space between the housing and the well bore, a support pipe connected to the upper end of said housing for supporting said housing and conducting a fluid therethrough to the housing, a tubular member in said housing and. connected thereto, a hollow shaft extending through said tubular member and extending into said support pipe, means connecting said hollow shaft to said housing for rotation relative thereto, motor impeller blades on said shaft and within said tubular member, said hollow shaft having outlet openings therein below said blades whereby fluid flowing down said support pipe through said hollow shaft will flow through said outlet openings and into said tubular member to rotate said shaft and the blades thereon, a shaft connected to the lower end of said hollow shaft and pump impeller blades thereon adapted to rotate upon rotation of said hollow shaft whereby well fluid is caused to flow upwardly in said housing.

8. The structure set forth in claim 7, including a means connecting said tubular member to said housing for rotation relative thereto, a sleeve connected to the lower end of said tubular member for rotation therewith, and pump blades on said sleeve cooperating with said pump blades on said shaft to pump fluid upwardly in said housing.

References Cited in the file of this patent UNITED STATES PATENTS Miller Nov. 12, Chubb Oct. 22, Amtrobus Feb. 26, Kay Mar. 2, Woock May 18, Eich Jan. 3, Bowlzer Apr. 29, Roder May 20, Morris Sept. 6, Bigelow Jan. 17, Bowen et al Oct. 31,

FOREIGN PATENTS Germany Sept. 13, France Mar. 11, Great Britain Dec. 30, 

